Radial pump and radial motor hydraulic transmission



T. MLLER Feb.- 12, 1952 2 SHEETS-SHEET l Filed Aug. 29, 1947 o y www, I v 1W H1 D L L W 6 lj 4 w 5 W w 3 N a W. y y 2 J 3 J w L@ 3 Hf., rh 4 La d w 7 )of E 1;:7 g2 M In F W UM wi T1 7 mi E of@ W 5 y 2 wwf/ m 3 T. MLLER Feb. 12, 1952 RADIAL PUMP AND RADIAL MOTOR HYDRAULIC TRANSMISSION 2 SHEETS- SHEET 2 Filed Aug. 29, 1947 IWUISWZZW' Themoid M' ibwnegs atented el). 12,

RADIAL PUMP AND RADIAL MOTOR HYDRAULIC TRANSMISSION Theodor Mller, Winterthur, Switzerland, as-

signor to Schweizerische Lokomotivund Maschinenfabrik, Winterthur, Switzerland Application August 29, 1947, Serial No. 771,317 v In Switzerland July 13, 1942 Section 1, Public Law 690, August 8, 1946 Patent expires July 13, 1962 (Cl. (S-53) 4 Claims. v l v This invention relates torpiston operated hydraulic transmissions, comprising a primary liquid pump unit and a secondary liquid motor unit with so-called divided output which may be termed hydraulic coupling transmissions for the reason that in adjusting the stroke of the secondary part (motor part) to zero the transmission can operate as a transmission in that the liquid then enclosed in the primary part (pump part), operating at constant or invariable stroke, allows of transmitting the driving torque of' the motor directly to the driven shaft.

With such transmissions 'it is known to arrange the cylinder blocks of the primary and secondary part that are provided with radial cylinder arrangements (spider shape) in a'common rotatable casing upon which act the piston thrusts of the primary and secondary part. rIhe control of the liquid circulation is effected in such an arrangement by the piston, themselves establishing communication, via openings in sliding pads carried by the pistons, with the liquid carrying spaces in said common casing. The adjustment of the eccentricity of the secondary part is elected by eccentric straps. l

It is further known to unite the radial cylinder arrangements of the primary and secondary part o-f such gearings into a single spider shaped structure in such manner that the cylinders lie in a common plane with the cylinder heads of` the pump cylinders facing outwardly and those of the motor cylinders facing inwardly, rotary control valves being provided one of which serves as the driving shaft while the other remains 'lxed in position. Readjustment of the eccentricity of the motor part (secondaryvv part) isefected by displacement of the rotatable casing surrounding the radial cylinder assembly. Although in such arrangements the control is improved the arrangement of the secondary cylinders results in highly irregular liquid induction which brings with it the risk of the setting up of hammering. Furthermore the cylinder clearance' becomes very lgreat and the presence of a roller bearing of large diameter for the rotatable casing on the side of the transmission on which the control means are arranged is for practical reasons hardly feasible.

Another proposed arrangement in which the primary cylinder block andthe secondary cylinder block are rmly connected with each other cannot be considered as a complete solution of the problem involved either for the reason that a practicable way for carrying out the liquid control and the mounting of the shafts'andcylinder blocks has not been shown;

The invention consists in a hydraulic transmission in which radial cylinder arrangements of a primary pump part 4and a secondary motor part are accommodated in a common rotatable casing to which the pistons of the pump part and the motor part are connected and the secondary radial cylinder arrangement is rotatably mounted on a bearing plug in overhung relation to a xed casing, characterised by the provision of a control device @for the cylinders in which the liquid passages are included in the bearing plugs (e. g. 8a,

3) on which the radial cylinder arrangements of the pump part and the motor part are rotatably mounted.

By this ymeans the advantages inherent in the control by means of rotary valves, i. e., large cross sections together with slight leakage losses are put into useful service. Furthermore, the cumbersome roller bearing on the side of the secondary part with adjustability of stroke is reduced to a practicable size for the reason that the control ducts of the pump operating at constant stroke and those of the motor part operating at variable stroke need no longer both be accommodated within this roller bearing but only `those of the secondary part.

Two exemplications of the transmission according to the invention are illustrated, by way of example only, in the accompanying drawings, in which:

Fig. 1 is a sectional elevation of a first exemplification;

Fig. 2 shows a sectional top plan view inclusive of a displaceable control plug;

Fig. 3 shows an elevation partly in section of a second exemplilcation;

Fig. 4 is an enlarged, partial cross section of the control plug of the secondary part on the line IV--IV in Fig. 2.

Fig. 5 is a cross sectional view on the line V-V of Fig. 1.

Fig. 6 is a cross sectional view on the line VI-VI of Fig. 1.

In a stationary casing I a rotatable casing l including the two radial cylinder arrangements 2, 3 of the pump part and the motor part respectively is journaled in a slide bearing 5 and a large roller bearing The pump crankshaft 8 by means of two ball bearings I is rotatably mounted in the rotatable casing 4, and the pump stroke is invariable. On an eccentric portion 8a of the crankshaft 8 is-rotatably mounted the radial cylinder arrangement 2 of the pump the pistons 9 of which are pivoted to the casing I! by means of connecting rods I0. The radial cylinder arrangement 2 and the casing 4 are coupled to each other` by three auxiliary cranks 2a the eccentricity of which is equal to that of the crank 8a, Fig. 5.

The crankshaft is provided on one side with an extension II on which a driving ange I2 is arranged. This shaft protrudes through the control plug I3 on which the secondary radial cylinder arrangement 3 of the motor part isV rotatably mounted. On the other side of the crankshaft an extension I4 is providedV in which two passages 2| and I5 for conveying working liquid into and from the pump cylinder are accommodated. The liquid delivery passes through the passage I5 in the shaft I4 and a port -IB in the bearing pin 4a of the casing 4 over into an annu,- lar passage I1 communicating with a pressure equalising Vessel I8. The reference numeral I9 denotes a suction pressure equalising vessel communicating with an annular passage from which the liquid is conducted through the passage 2 I in the shaft I4 to thepump cylinder 2.

yThe displaceable control plug I3 ofthe secondary part is as shown in Figs. 1, 2 and 4 horizontally displaceably arranged in a slide guide 22 in Va bearing carrier shield 23 and is guided by means of appertaining studs 2,4. in guides 25 on the covering shield 2.3: transversely of its longitudinal axis. The plug I3 can be adjusted by anyV suitable means. 25 are Yconstructed as closed cylindrical pockets theguide plug can be shifted by means of pres.- sure oil selectively acting vupon the respective ends of the guide studs 24 then being in the form of. servomotor 'plungers operating with the radial cylinder arrangement 3 ofV the motor part are pivotally connected to the common casing 4 by means of connecting rods 33. The cylinders 3 andthe casing 4 are interconnected by a coupling'which ensures synchronous operation of.V these two parts, Fig. 6. For this vpurpose the casing 4 and the cylinder block 3 ofthe secondary part are coupledwith each other by the connecting links 40, 4I, 4,2 hingedly connectedto the motor casing 3 and the casing 4, the type ofthis linkage being known under vthe name of Ganz coupling. The bolts 43 of the bell crankY levers 40 are rigid with the cylinder block 3, andthe bolts 44 are rigid with the casing 4. This coupling permits in known manner to vary the eccentricity of the axesy of rotation of the radial cylinder-block 3 and of the casing 4 of the secondary part, whereby these members are obligedto turn in a completely synchronous manner.

In the control plug I3 passages 26` and 21 for respectively discharging and supplying of working liquid are arranged together with a throughbore 28 in which the driving shaft II is housed. The liquid passages 26, 21 are continued across the slide guide surfaces into passages 33, 3 4,in the casing covering shield 23 (see Fig. 4), these passages 33, 34 being soarranged that at maximum eccentricity c of the control plug I3 of the secondary part the liquid is given maximum cross sectional area of free passage and most smooth guidance in passing over into the bearing carrier shield 23.

Said passages are further so arranged that the pressure P (Fig. l) exerted on the radialcylinclei` arrangement 3 and the control plug I3 through the connecting rods 30, urges the control plug at the point 31 and at the place of transition 38 of the passage 21 against the surface of the slide guide, thereby preventing leakage losses at this If, for example, the guides 'Die pistons co- :N

. motor.

place. The passages 33, 34 communicate by conduits 45 and 46 with the annular passages 20 and I1, respectively. A relieving groove communicating withthe pressure space of the transmission may be arranged at' the point 31 for reducing the bearing pressure at this point.

When the control plug I3 is coaxial with the axis ofrotation of the casing 4 the motor part has no liquid admitted thereto so that the pump vpart is kept from delivering, in consequence whereof, by eiectof the pressure oil present therein, directtransmission of power takes place from thesh'aftll l"to the casing 4 and to the driven shaft 4d., 3l. If the control plug I3 is displaced `from central position up to the maximum eccentricity e a maximum amount of pressure liquidl'is admitted to the motor part so as to impart an additional torque of maximum intens'ity to the rotating casing 4, whereas on the other hand the pump 2 runs at maximum relative speed'and thedrivenV shaft 4a, 3l runs slow- 1y, the torque delivered by the shaft IIk being then transmitted directly tothe driven-shaft via the pump cylinders.

. If it is` desired to4 let the driven shaft 3 I run at stilllower speed than corresponds to themaximum absorbing` capacity ofthe cylinders 3l a rotary valve 32 for` passing the excess oil directly into the suctionvspaceis opened by whichA means the speed` of revolution of the driven shaft is adjusted down tozero while the torque is maintained at maximum valide` If the axis ofrotation of; the cylinder arrangement 3l is shifted outl of its central position in the direction opposite to the Aposition occupied for low speed running the torque effected by the secondary part of the. casing 4 does no longer act in; the same direction as the torque of the driving shaft derived from the primary part but is opposed to the latter-torque. The driven shaft 4a. 3l receives thereby a torque which is smaller thanthe driving. torquev and runs at a higher speed than driving shaft. 'The secondary part works then as pump and theV primary part as If the axis Qf.. rotation of the casing 4 isfurther displaced in the same direction and so far` that the countertorquer of the secondary partY surpasses the torque of the primary part reverse motion is obtained.

The exampleshown in Eig. Bvaries from that describedabovein that the transmission of torque from the casing 4..is effected by means of a toothed rim v35 which is fastened to the latter andmeshes in-a gear 36 on the driven shaft 3Ia. The driving flange -I2A is indistinction from Fig. 1 notmounted on a shaft stub protruding through ythevcontrol plugV I3 but is arranged in the'p'ump crank shaft `I4 shown indotted lines which includes" the suction and pressure conduits-2 I and lurespectively for the lworking liquid. Otherwise theY construction and operation of the gearingshown in Fig. tis the same as that 'described'l in connection with the gearing shown in Figs. V1 to 3. l'

A modification of thearrangement shown in Fig. 4 may,y consistfin'arranging only the pressurepas'sage "I5 -in thestub lshaft I4 and shifting` the suction conduit to the other projecting stubshaft' onf the'` crankshaft 8. which isrprolonged upv to'.the`.'contro1 plug I3, direct communication beingfprovided through the end face 3920i:'thedisplacablecontrol plug I3 with the suction'passagesQZ'S arranged at this place.

`Drivingwmovementmayf.befimparted to the gearing at 3| instead of at I2. This mode of `op eration permits of obtaining aconstant torque at the iiange I2 when the oil pressure is main- Atained constant within the gearing. This torque is (further obtained at a continually variable speed 'of revolution of this iiange from zero up to direct vdrive while the iianges I2 and 3I run at equal speed of revolution or the former faster than the latter without requiring the circulation control valve 32 to be openedat low speed tof revolution. j

1. In a hydraulic transmission, the combination of a stationary case, a driving shaft having an eccentric rotatably mounted in said case, a pump part of iixed stroke having a cylinder block rotatably mounted on said eccentric, a bearing pin projecting inwardly from one end of said case, said pin having a square portion slidably mounted in a guide slot provided in said case end for movement transversely to the pin axis, a motor part of variable stroke having a cylinder block rotatably mounted on the free end of said pin, a casing rotatably mounted Within said case and surrounding the cylinder blocks of said pump part and motor part, said casing having a partition extending between said cylinder blocks of the pump part and motor part, a driven shaft connected to said rotatable casing, said pump part and motor part being of the expansible chamber type having radial cylinders formed in said cylinder blocks, reciprocating pistons, and piston rods pivotally connected to said rotatable casing. a plurality of auxiliary cranks for coupling the pump part cylinder block with said rotatable casing, the eccentricity of said cranks being the same as that of the eccentric of said driving shaft, coupling means for interconnecting the cylinder block of the motor part and said rotatable casing to provide for synchronous rotation of said motor part cylinder block and said rotatable casing, said driving shaft being provided with suction and delivery ducts for conveying working liquid to and from the cylinders of said pump part, said transversely movable bearing pin being provided with suction and delivery ducts for conveying working liquid to and from the cylinders of said pump part, said transversely movable bearing pin being provided with suction and delivery ducts for conveying working liquid to and from the cylinders of said motor part, conduits for interconnecting the delivery duct of one part to the suction duct of the other part, and means for moving said bearing pin in said guide slot transversely relatively to the driving shaft for adjusting the piston stroke of said motor part.

2. In a hydraulic transmission, the combination of a stationary case, a driving shaft having an eccentric and extending through said case. a pump part of xed stroke having a cylinder block rotatably mounted on said eccentric, a bearing pin projecting inwardly from one end wall of said case, said pin having a square portion slidably mounted in said end wall for movement transversely to the pin axis, a motor part of variable stroke having a cylinder block rotatably mounted on the free end of said pin, a casing rotatably mounted within said case and surrounding said cylinder blocks of the pump part and motor part, said rotatable casing having a partition extending between said cylinder blocks of the pump and motor parts, a. driven shaft rigid with said rotatable casing, said pump part and motor part being of the' expansible chamber type having radial cylinders formed in said cylinder blocks, reciprocating pistons and piston rods pivotally connected to said rotatable casing, auxiliary cranks for coupling the pump part cylinder block to said rotatable casing, the eccentricity of said cranks being the same as that of the eccentric on said driving shaft, coupling means for interconnecting the cylinder block of the motor part and said rotatable casing to providey for, synchronous rotation of said cylinder block and casing. said driving shaft being provided with suction and delivery ducts for conveying working liquid to and from the cylinders of the pump part, said bearing pin being provided with suction and delivery ducts for conveying working liquid to and from the cylinders of said motor part, two air vessels carried outside of the stationary casing and communicating with said suction duct and said delivery duct, respectively, provided in the driving shaft, a conduit for connecting the delivery duct of the pump part to the suction duct of the motor part, a conduit for connecting the suction duct of ,the pump part to the delivery duct of the motor part, means for moving said bearing pin in said guide slot transversely relatively to the driving shaft for adjusting the piston stroke of the motor part. and manually operable valve means for establishing communication between said two air vessels.

3. In a hydraulic transmission, the combination of a stationary case, a driving shaft having an eccentric rotatably mounted in said case, a pump part of fixed stroke rotatably mounted on said eccentric, a bearing pin projecting inwardly from one end wall of said case in a direction parallel to the driving shaft, said pin having a square portion slidably mounted in a guide slot provided in said end wall for movement of the pin transversely of the axis of the driving shaft. a motor part of variable stroke rotatably mounted on the free end of said bearing pin, a casing rotatably mounted within said stationary case and surrounding said pump part and motor part. a driven shaft connected to said rotatable casing, said pump part and motor part having radial cylinders, reciprocating pistons and piston rods pivotally connected to said rotatable casing, said driving shaft being provided with suction and delivery ducts for conveying liquid to and from said pump part, said bearing pin being provided with suction and delivery ducts for conveying liquid to and from said motor part, said end wall of the stationary case being provided with suction and delivery ducts communicating across the guide surfaces of said square portion of the bearing pin and of said guide slot with the suction and delivery ducts, respectively, of said bearing pin, the suction and delivery ducts in said end wall communicating with said delivery and suction ducts, respectively, provided in the driving shaft, and means on said end wall for slidably guiding said bearing pin transversely to the longitudinal axis thereof and for preventing longitudinal movement of the pin.

4. Hydraulic transmission mechanism as claimed in claim 3, in which said rotatable casingis provided with a gear crown meshing with a gear wheel on the driven shaft'permitting the ITHEODQR REEERENQES. Crum.

.Number Name Date Conradson June l27,"19-16 VBeatty fDec. 5, 1922 B1sc1iof;' Dec", 271g 193,8 de viuiers Apr.y 15,y 1.941 

